Machine tool



Jan. 19, 1937. LANGE 2,068,552

MACHINE TOOL 4 Filed Feb. 26, 1955 '8 Sheets-Sheet 1 lamilimrm 1N VENT OR. MAX film ATTORNEYS M. E. LANGE Jan. 19, 1937,

MACHINE TOOL Filed Feb. 26, 1955 8 Sheets-Sheet 2 R O T N E V m MAXZZA/YGE Y jfww fiz ATTORNEYS M. E. LANGE Jan 19, 1937.

' MACHINE TOOL I Filed Feb. 26, 1935 8 Sheets-Sheet 3 INVENTOR. /74x 5 ln/va's 14M Mafia ATTORNEY5 M. E. LANGE Jan. 19, 1937.

.MAcHmE TOOL Filed Feb. 26, 1955 8 Sheets-Sheet 4 INVENTOR. M rx Ell/was BY %%g% ATTORNEYS Jan. 19, 1937. LANGE 2,068,552

MACHINE TOOL Filed Feb. 26, 1935 8 Sheets-Sheet 5 I l l mg I INVENTOR.

MAX til/1W6:

ATTORNEYS M. E. LANGE MACHINE TOOL Jan. 19,1937.

Filed Feb. 26, 1935 8 Sheets-Sheet 6 ATTORNEY! Jan. 19, 1937; M; E. LANGE 8,

MACHINE TOOL Filed Feb. 26, 1935 8 Sheets-Sheet 7 INVENTOR.

Max .5 L/4N6E g I BY ATTORNEYS Jan. 19, 1937. LANGE 2,068,552

MACHINE TOOL Filed Feb. 26, 1955 a Sheets-Sheet a Hill] All?!" ATTORNEYS Patented Jan. 19, 1937 UNITED STATES PATENT OFFICE MACHINE TOOL Application February 26, 1935, Serial No. 8,319

49 Claims.

This invention relates to a machine tool and particularly to means for controlling the operation of a movable part of a machine tool, as, for example, controlling the speeds of operation and the starting, stopping, and reversing of said movable part.

An object of the invention is to provide an improved means for controlling the operation of a movable part of a machine tool.

Another object is to provide improved means for controlling the operation of the spindle of a machine tool.

Another object is to provide improved means for controlling the speeds of operation and the starting, stopping, and reversing of a movable part of a machine tool.

Another object is to provide in a machine tool improved means for controlling the speeds of operation and the starting, stopping, and reversing of the spindle thereof.

Another object is 4: provide, in a machine tool having a part movable at different speeds and abraking mechanism for stopping the drive of said part, means whereby the braking resistance of said mechanism may be preselected during one speed of movement of said part for the next speed of movement thereof.

Another object is to provide in a machine tool having a part movable at different speeds and having a braking mechanism for stopping the drive of said part, a single control member for applying and releasing said braking mechanism, for preselecting during one speed of movement of said part a different braking resistance for.

said braking mechanism for the next speed of movement of the part, and for effecting the Change to said preselected braking resistance.

Another object is to provide in a machine tool improved means for controlling the speeds of operation of a movable part of the machine and the braking thereof when the movement of the part is to be stopped.

A further object is to provide in a machine tool improved means for controlling the speeds of operation and the starting, stopping, and reversing of a movable part of the machine and the braking of said part when its movementis to be stopped.

. A further object is to provide in a machine tool means for controlling the speeds of operation and the starting. stopping. and. reversing of a movable part of the machine and including a single control member for said means.

Another object is to provide in a machine tool improved means for controlling the speeds of cperation and the starting, stopping, and reversing of a movable part of the machine and for imposing upon said part, when its movement is to be stopped, a variable braking resistance proportional to its speed of movement. 5

Another object is to provide in a machine tool a single .control member for controlling and actuating a preselecting speed change gear device and the stop, start, and reverse clutch of the drive for a movable part of the machine tool.

Another object is to provide in a machine tool a single control member for controlling and actuating a preselecting speed change gear device and the stop, start, and reverse clutch of the drive for a movable part of the tool and for imposing upon said part, when its movement is to be stopped, a variable braking resistance proportional to its speed of movement.

Another object is to provide in a machine tool preselecting means for the speed change gears of the drive of a movable part of the machine tool and wherein said preselecting means controls the imposition upon said part, when its movement is to be stopped, of a variable braking resistance proportionate to the speeds of movement of the part.

A further object is to provide in a machine tool a single control member for controlling and actuating a preselecting speed change gear device and the start, stop, and reverse clutch of the spindle drive.

Another object is to provide in a machine tool a single control member for controlling and actuating a preselecting speed change gear device and the stop, start, and reverse clutch of the spindle drive and wherein the preselecting device controls the imposition upon the spindle drive when it is to be stopped of a variable braking resistance directly proportional to the speed of operation of the spindle. 40

Another object is to provide in a, machine tool preselecting and gear shifting means for the drive of a movable part thereof and including power actuated gear shifting members.

Further and additional objects and advantages not hereinbefore set forth will become apparent hereinafter during the detailed description which is to follow of several embodiments of the invention.

In order to illustrate the invention and sevcral mechanical embodiments thereof, the invention has been shown herein as applied to the head stock of a lathe and as controlling the operation of the spindle thereof, but it should be understood that the invention may be applied to other movable parts of a machine tool having a speed change drive and forward and reverse directions of movement.

Referring to the accompanying drawings:

Fig. 1 is an elevational view of the head stock of a lathe and is taken in a direction looking toward the spindle nose;

Fig. 2 is a top plan view of the head stock shown in Fig. 1 with certain portions at the upper left-hand corner of the head stock broken away and shown in section;

Fig. 3 is a detail sectional view taken substan tially on line 33 of Fig. 2, looking in the direction of the arrows;

Fig. 4 is an irregular vertical sectional view through the headstock and is taken substantially on lines 44 of Figs. 2 and 8, looking in the direction of the arrows;

Fig. 5 is a fragmentary vertical sectional view taken substantially on lines 5-5 of Figs. 2 and 8, looking in the direction of the arrows;

Fig. 6 is an irregular detail vertical sectional view taken substantially on line 66 of Fig. 4, looking in the direction of the arrows;

Fig. 7 is a detached detail view of a part of the mechanism shown in Fig. 4;

Fig. 8 is a horizontal sectional view taken substantially on line 8-8 of Fig. 4, looking in the direction of the arrows;

Fig. 9 is a fragmentary irregular horizontal sectional view taken substantially on line 99 of Fig. 4, looking in the direction of the arrows;

Fig. 10 is a detached view of a portion of the parts illustrated at the left-hand end of Fig. 8,

said parts however being in a different position in Fig. 10 than in Fig. 8;

Fig. 11 is a detail sectional view taken substantially on line lI-H of Fig. 10, looking in the direction of the arrows;

Fig. 12 is a detail sectional view taken substantially on line l2--l2 of Fig. 10, looking in the direction of the arrows;

Fig. 13 is a developed view of the spools shown in Figs. 8, 9, and 10, and illustrates diagrammatically various positions of the gear shift levers which are located between the spools;

Fig. 14 is a diagrammatic illustration of the speed change g aring and drive for the spindle in the head;

Fig. 15 is a view, partly in elevation and partly in section, of the head stock of a lathe and is taken substantially on line I5-l 5 of Fig. 2, looking in the direction of the arrows, and illustrates the brake mechanism for the spindle drive;

Fig. 16 is a fragmentary sectional view taken substantially on line l6-l6 of Fig. 15, looking in the direction of the arrows;

Fig. 16a is a detached detail sectional view taken substantially on line l6al6a of Fig. 15;

Fig. 16b is a developed view of the spools for operating the presetting means for the brake mechanism;

Fig. 17 is a fragmentary sectional view taken substantially on line 11-11 of Fig. 15, looking in the direction of the arrows;

Fig. 18 illustrates a modified form of construction from that previously illustrated and is a fragmentary view of a head stock of a lathe partly in elevation and partly in section, the sec-. tion being taken substantially on line I8-l8 of Fig. 20, looking in the direction of the arrows;

Fig. 19 is a fragmentary sectional view of the head stock and is taken substantially on line l9-l9 of Fig. 20, looking in the direction of the arrows;

Fig. 20 is a fragmentary top plan view of th head stock partially in section, the section be ing taken on line 20-20 of Fig. 18, looking in th direction of the arrows;

Fig. 21 is a fragmentary top plan view of th head stock and shows the parts which are abov the sectional portion of Fig, 20;

Fig. 22 is a developed view of the spools fc operating the gear shifting mechanism for th three-step gear cone of the drive in the head 2 shown in Fig. 14;

Fig. 23 is a developed view of the spools fc operating the shifting members for the iron two-step gear cone as shown in Fig. 14;

Fig. 24 is a developed view of the spools fc operating the shifting members for the rear two step gear cone shown in Fig. 14;

Fig. 25 is a fragmentary irregular section: view taken substantially on line 25--25 of Fit 18, looking in the direction of the arrows;

Fig. 26 illustrates a modified form ofcon struction from those previously illustrated and i a fragmentary top plan view of a head stock of lathe partly in section; and

Fig. 27 is an end elevational view of the hea stock shown in Fig. 26 taken looking toward th nose of the spindle and is partly in section.

Referring to Fig. 1, there is shown a head stoc 30 of a lathe and a cover 30a therefor, a-portio of the bed 3| thereof, and the nose of a rotat able work spindle 32 which is mounted in th head.

As will be understood in the art, the rotatabl work spindle 32 is driven at different speeds b means of change speed gearing arranged in th head and its rotation is stopped, started, an reversed by means of clutches likewise located i the head 30.

Reference should first be made to Fig. 14 of th drawings wherein a train of change speed gear ing for driving the spindle 32 is shown, as a1 also the clutches for starting, stopping, an reversing the rotation of the spindle.

A pulley 33 is fixed to a shaft 34 rotatabl mounted in the head and said pulley is prefei ably driven by a belt drive from a two-spee motor (not shown) so that the work spindle wi have a series of high speed operations and series of low speed operations, depending upo the speed of operation of the motor. It will i: understood that a conveniently located an operated control switch for the motor is prc vided on the head.

A pair of multiple disc clutches 35 are mounte on the shaft 34 and a clutch operating membi 36 is splined to the shaft between the clutches 3 to be moved into clutching engagement wit either one of said clutches to obtain forward reverse drives for the spindle or to be positione in neutral out of clutching engagement with bot clutches to stop the rotation of the spindle. I will be understood that the parts of the clutch 35 carrying the gears 31 and 38 are freel rotatable on the shaft 34 until the parts by whic they are carried are clutched to the member 3 The gear 31 constantly meshes with a gear 3 fixed to a shaft 40 arranged in the head i parallel relationship to the shaft 34. The gee 38 meshes with an idler gear 4| rotatable on shaft 4la (see Fig. 4) which in turn meshes wit a gear 42 likewise fixed to the shaft 40. Intel mediate the gears 39 and 42 a three-step gee cone is splined to the shaft 40 so as to rotai therewith and slide thereon and comprises tr gears 43, 44, and 45.

the gears 46, 41, and 48 being fixed to a shaft 49 rotatably mounted in the head and capable of having imparted thereto,three different speeds of rotation in both a forward and a reverse direction.-

The gear 48 constantly meshes with a gear 50 carried by a sleeve freely rotatable on the spindle 32 but held against axial movement thereon. The sleeve 5| is provided with a second H gear 52 spaced axiallyof the spindle from the gear 50. meshed with a gear 53 of a two-step gear cone splined to a shaft 54 so as to rotate therewith but slide thereon; or the gear 52 on the sleeve 5| maymesh with the gear 55 of the said two-step gear cone when said cone has been shifted from the position shown in Fig. 14 to a position such as to bring the gears 52 and 55 into intermeshing relationship. It will be understood that the shaft 54 can be rotated through the two-step gear cone and the three-step gear cone at six different speeds in both the forward and reverse directions.

Asecond two-step gear cone is splined tothe shaft 54 and comprises a gear 56 and a gear 51. This last mentioned two-step gear cone may be shifted in one direction to bring the gear 56 into intermeshing relationship with a gear 58 fixed to the'spindle 32 or it may be shifted in the opposite direction to bring the gear 51' into intermeshing relationship with a gear 59 also fixed to the spindle 32. It will thus be seen that through the two two-step gear cones and the three-step gear cone the spindle 32 may be driven at twelve different speeds in both the forward and reverse directions. It will be remembered that a twospeed motor preferably is used to drive the shaft 34 through the pulley 33 and thus the spindle 32' may be driven at any one speed in two series of twelve speeds each, or at twenty-four different speeds in both the forward and the reverse directions. I

The construction thus far described is conventional and does not form any part of the present invention except so far as it has cooperating relationship with the construction later to be described.

The clutch member 36 is shifted by means of a yoke member 66 integral with a sleeve 66a slidable on a rod 6| fixedly mounted in brackets located within the head and carried by the cover 36a, see Figs. 4 and 8. The yoke member straddles a groove in the clutch member 36 and is actuated endwise of the rod 6| by a short lever 62 having its end between lugs formed on the member 60, and said lever 62 is fixed to the lower end of an oscillatable vertically extending shaft 63 mounted adjacent the top of the head in the cover 36a. (see Fig. 4) to which reference will later be made. It will be understood that, if the shaft 63 is rocked in one direction or the other,- the clutch member 36 will clutch the member and the gear 38 or the member 35 and the gear 31 to the pulley shaft 34.

The three-step gear cone on the shaft is shifted by means of a yoke member 64 slidably mounted on the shaft 4la'which carries the idler gear 4 I, which yoke member has a portion at one end straddling the middle gear of the three-step gear cone and an angularly disposed portion at its opposite end straddling the end .of a lever 65 The gear 56 on the sleeve 5I'may bewhich has its opposite end fixed to the lower end of an oscillatable, vertically extending shaft 66 carried by the cover 36a. The shaft 66, adjacent its upper end. has fixed thereto a lever 6! later to be referred to. It will be understood that, when the shaft 66 is rocked, the member 64 will be moved endwise of the shaft 4la'to shift the three-step gear cone to any of its three operative positions.

The rear two-step gear cone (the upper gear coneshown in Fig. 14) on the shaft 54 is shifted to either of its two operative positions by means of a lever 68loosely mounted on the shaft 66 above the lever 65 and having at its end a shoe 69 straddling the gear 55.

The other or front two-step gear cone on the shaft 54, that is. the lower two step gear cone as viewed in Fig. 14, is shifted to ither of its two operative positions by means of a lever 10 fixed to a vertically extending rockable shaft H carried by the cover 36a of the head (see Fig. 5), which lever is provided at its end with a shoe 72- that straddles the gear 56 of the two-step gear cone.

The shaft H adjacent its upper end has secured thereto a short lever 73 the outer end of which is pivotally connected to one endof a link 14. The opposite end of the link l4'is pivotally connected to the upper side and at one end of an angularly bent arm 15, the opposite end of which arm is pivotally mounted 'on the shaft 66 abovethe short lever arm 61 previously referred to, see

Figs. 4 and 8. It will be seen that when the arm 15 is moved in opposite directions the shaft H will be rocked through the link 74 and the lever arm 13 and hence movement of the arm 15 will effect a shifting movement of the front two-step gear cone on the shaft 54 to one or the other of its two operative positions.

The levers 61 and 68 and the arm 75 are provided with pins 16, TI, and 18, respectively,

shown in the drawings as being substantially rectangular in cross-section, which pins are equally spaced radially. from a common center and are.

circularly spaced in predetermined relationship as shown in Fig. 4. The pins 16, 11, and |8 lie intermediate a pair of spools 19 and 19a mounted I on a shaft 'so as to slide therealong and rotate therewith, said shaft 80 being the common center from which the pins are radially equally spaced.

In Fig. 8 the spools are shown in their most inward position upon the shaft 86, while in Figs. 9 and 10 the spools are illustrated in. their most outward or separated position on the shaft 80. The spools l9 and 19a can be moved along the shaft 80 toward each other an equal distance from their outer positions, as shown in Figs. 9 and 10, by means later to be more fully explained, the movement of the spools toward each other acting to shift the pins 16; TI, and 18 to effect a shifting of the levers and the arm carrying said pins and in turn a shifting of the various gear cones previously referred to.

a shorter projection on the other spool and the spools are moved inwardly an equal distance, it will be understood that if one of the pins is engaged by the long projectionthe pin will be toward the spool that has the short projection.

In the instance where projections of equal length are brought into engagement with the pin when the spools are moved toward each other an equal distance, it will be clearly seen that the pin will .be positioned by the projections in a central location with respect to the spools. Thus a plurality of different arrangements of the projections on the spools may be effected by giving the. spools a step-by-step rotative movement when the spools are in their outermost position so that a movement of the spools an equal distance inwardly toward each other will result in predetermined movements to or positioning of the pins 16, 11, and 18, and, therefore, a predeter mined shifting of the gear cones in thehead and a consequent changing of the speed of operation of the work spindle.

It is necessary, in order to shift the pin that actuates the three-step gear cone to three operative positions, that the spools be provided with cooperating long and short projections, projections of equal length, and short and long projections, respectively, so that the pin will be moved to one side or the other of a central position relative to the spools or may be moved into said central position. Inasmuch as the rear twostep gear cone need only be moved into two operative positions, the spools should be provided with cooperating sets of long and short projections and cooperating sets of short and long projections for shifting the pin associated with said two-step gear cone, it being understood that the pin need only be moved to one or the other of two working positions. It is necessary to move the front two-step gear cone to a neutral position to disconnect the work spindle from its gear drive to permit the spindle to rotate freely for purposes of loading.- Therefore, in one position of the step-by-step rotative adjustment of the spools, the same should be provided with a pair of projections of equal length which engage the pin associated with the front two-step gear cone to bring it into neutral position, otherwise the spools are provided with cooperating sets of long and short projections and short and long projections for shifting the said pin to either one or the other of its two working positions, similar to the provision made for the shifting of the pin associated with the rear two-step gear cone, as previously explained.

Inasmuch as there has been illustrated a work spindle having twelve different speeds of operation in the forward and reverse directions, it will be necessary to impart to the spools thirteen equal step-by-step increments of rotation to complete one revolution of the spools, twelve of such steps of rotation setting the spools for the twelve different speeds of the work spindle, while the thirteenth step of rotation of the spools sets the latter to effect the shifting of the front two-step gear cone into neutral position.

Inasmuch as the spools are given thirteen successive steps of rotative adjustment in a single projections of the three series arranged in groups of three, wherefore, during the step-by-step rotation of the spools, the projections of the series will always be in the same relationship with each other.

The spools 19 and 19a can be manually indexed step-by-step, as will now be explained, or they can be indexed by power, as will later be explained.

Assuming that the work spindle 32 has just been loaded with' a new work piece and the machine is at rest, and the front two-step gear cone is in neutral position, the dial 8| on the front of the cover 30a of the head will be in such position that the letter N on its circumference will coincide with a pointer line on the pointer 82 and indicates that the work spindle is not connected to the gear 'drive, and the front two-step gear cone is in neutral position.

The dial 8| is carried by a shaft 83 rotatably mounted in the cover and provided with a spiral gear 84 meshingwith a spiral gear 85 on the shaft 88 (see Figs. 9 and 15), wherefore rotation of the dial 8| and the shaft 83 causes a rotation of the shaft and a rotation of the spools 19 and 19a carried thereby. A complete rotation of thedial 8| from the position shown in Fig. 1 will effect a complete rotation of the spools I9 and 19a, while a step-by-step rotation of the dial to bring the different numerals on its circumference in line with the pointer 82 will effect a similar step-bystep rotation of the spools, such numerals indieach of the two series obtained when the motor is operated at its high or low speed.

Assuming that the front two-step gear cone is in neutral position and the rear two-step gear cone is in its most forward position, while the three-step gear cone is in its most rearward position, as viewed in Fig. 14, then the pins 16, I1, and 18 will occupy the positions shown in full lines in Fig. 13. The dial 8| is now turned to move the spools one step of rotation, and when afterwards the spools are moved inwardly to shift the pins, the pin 18, in the present instance, will be shifted to shift the front two-step gear cone forwardly into mesh with the gear 59 carried by the spindle, while the pins 11 and 16 will remain in the positions they were previously in. Assuming that the dial and the spools are turned another step for the next speed, the pins 11 and 18 will not be shifted when the spools are moved inwardly, while the pin 16 will be moved in a manner to effect a shifting of the three-step gear cone from its most rearward position to its most forward position, that is, the gears 45 and 48 will be disengaged and the gears 43 and 46 brought into mesh. It will be clear that any successive movement of the dial will effect a step-by-step' movement of the spools and thus the pins will be shifted in predetermined ways as the spools are brought inwardly to effect a shifting of the variousgear cones to provide the different speeds of operation for the work spindle. In practice, it will be understood that the dial is rotated to the desired speed of operation which in many instances will impart rotative movement to the spools through a number of their rotative steps of adjustment.

The spools l9 and 19a are provided with annular grooves in the bases of which are formed thirteen depressions 86 corresponding to the number of steps of rotation that the spools are given in a complete movement of rotation. Forks 81 and 88 extend into the grooves with the fork 81 2,068,552 carrying a springpoint 89 engaging the depres-' sion 86 of the spool 79a and with the fork 88 carrying a locking pin 90 engaging the depression 86 of the spool I9, as will be explained hereinafter. The fork 81 is integral with a sleeve 9I slidably mounted on a rod 92 arranged horizontally in the cover 30a of the head while the fork 83 is integral with a similar sleeve 93 slidably mounted on a rod 94 spaced from but parallel to the rod 92.

When the spools I9 and 19a are in their most outward position, as indicated in Figs. 9 and 10,'

the locking pin 90 of the fork 88 registers with a recess 95 formed in the rod 94 to allow the pin 90 to move radially outwardly from a depression 86 into the recess 95 and permit the spools to be given their step-by-step indexing movement by rotating the dial 8I with the spring point 89 locating the dial for each step of movement. It will be seen that the lock pin 90 forms a safety device so that the spoolsmay be rotated only in their most outward positions where the projections on the spools will not contact with the pins I6, '11, and 18.

The sleeves SI and 93 are provided with upwardly extending portions 9Ia and 93a having transversely extending slots in which slidably engage shoes carried at the opposite ends of an equalizer bar 96 formed integral with the lower end of a vertically extending shaft 97 mounted for rocking movements in the cover 30a. of the head and projecting outwardly therefrom, see Figs. 4 and 10.

It will be apparent that when the shaft 91 is rocked in one direction or the other the spools 19 and 19a will be moved inwardly and outwardly an equal distance, since the arms of the equalizing bar 98 are of equal length.

The shaft 91, as previously explained, extends above the upper side of the cover of the head, and there is secured to said extending portion of the shaft to rock therewith a disc 98 having a threaded opening receiving the threaded end of a rod 99 constituting a lever, it being noted that the rod 99 can be adjusted relative to the disc 98 to provide for varying leverages.

The outer end of the rod 99 is pivotally connected to the threaded portion I of a two-part link, the other portion IOI of which is adapted to be adjustably screwed upon the portion I00 for varying the length of the link. The opposite end of the portion I 0| is pivotally connected to a fork I02 having a threaded extension which screws into a vertically extending threaded opening in the upper side of a hub member I03, the fit between the threaded extension and the opening being such that the extension will turn freely in the opening when the hub is turned and will allow an adjustment of the fork I02 for varying leverages.

The hub I03 straddles and is pivotally connected to a substantially U-shaped portion 53a formed on the previously mentioned shaft 63 and located above the upper side of the cover 3011 of the head, as clearly shown in Figs. 4, 5, and 6, thus allowing the hub I03 to rock about a horizontal axis.

The hub I03 is provided with a forward extension into which is secured the end of an operating member or lever I04 that projects above the cover 30a of the head and beyond the front side thereof within easy reach of the operator. It will be seen that by means of the lever I04 the hub I03 can be rocked about its pivotal connection to the portion 630. of the shaft 63 in a vertical direction. The movement of the lever I04 and the hub I03 in a vertical direction acts through the link I00--IOI and lever 99 to rock the disc 98 and shaft 91 to cause the equalizer bar 96 to effect an equal movement of the spools inwardly and outwardly, the upward.- movement of the lever I04 moving the spools outwardly to allow them to be indexed and the downward movement of the lever I04 moving the spools inwardly to shift one or more of the pins 16, TI, and I8 and consequently the gear cones in the head.

When the lever I04 is moved upwardly from a substantially horizontal position, as viewed in Fig. 5, to cause the spools to move outwardly and to a.low the dial 8| and. the spools to be turned to-select, a different speed for the work spindle, the lever I04 will be retained in its upper position by means of a friction shoe I 05 engaging the side of a block I06 located within the hub and pivotally mounted in the U-shaped portion 63a upon the same pivot as the hub. Downward movement of the lever I04 will bring the spools inwardly to shift the pins and the gear cones to change the speed of the work spindle and will also rock the hub I03 about its pivot and through the frictional engagement of the shoe I05 with the side of the block I06 will rock the latter downwardly to the position shown in Fig. 4.

The movement of the block I 06 downwardly compresses a spring I01 arranged in a recess in the block and engaging with the U-shaped portion 63a of the shaft 63 while the block abuts the portion 63a adjacent the lefthand end of the block as viewed in the drawings. The block I06 at its left-hand end, as viewed in Fig. 4, is provided with a tongue I06a which, when the block abuts the portion 630., extends into a segmental groove formed in the inner side of a stationary block I08 located within the hub I03 and secured to .the cover 30a, wherefore the control lever I04 may be moved horizontally in opposite directions to rock the shaft 63 and to engage the friction clutches 35 with the clutch member 36 for forward or reverse operation of the work spindle. When the control lever I04 is in the position it occupies when both of the friction clutches, previously referred to, are disengaged from the member 36, a notch I 08a in the stationary block I 08 is in alignment with the tongue I 06a of the block I 06 so that the spring I01 can move the block and 5' hub upwardly when the lever is released by the operator to bring the tongue I06a within the notch I 08a and thus hold the control lever I04 from horizontal movements and in neutral position with both clutches disengaged. seen that when the control lever has been moved to a neutral position and the operation of the spindle stopped the operator need merely take his hand from the control lever and it'will move automatically into the locked position just explained.

In order that the gear cones may not be shifted until the control lever has been brought to a neutral position, i. e., both friction clutches disengaged, the mechanism now to be described is employed.

The under side of the U-shaped portion 63a of the shaft 63 is provided with a depression 63b which, when the control lever is in the neutral position, registers with a locking pin I09 mounted 7' in an opening formed in the top of the cover of the head and engaging at its lower end an extension formed on the lever IIO of a two-part locking member, the other part of which is a lever III. It will be seen that the lever I II of It will be the two-part locking member is provided with ears pivoted upon a pin 2 while the lever H is pivoted upon the same pin 2 between the ears of the lever III. The lever IIO has an extension lI0a engaged by a spring I MD and normally held in contact with the upper endof the lever III by means of a spring H3. The lever IIO has a downwardly projecting extension 00 between which extension and the lever III is located-said spring H3. The lower end of the lever I I I is provided adjacent the spring I I3 with a laterally extending locking tooth Illa. The lever III also has at its lower end a rearwardiy projecting extension carrying at its end a laterally extending locking tooth II lb.

The locking tooth Illa, when the lever III is in the position shown in Figs. 4 and 8, is adapted to engage in one or the other of two recesses a formed in the arcuate edge of an extension I0b of the lever 10 to lock the lever I0 (see Fig. 5) in one or the other of the two positions it assumes after shifting the front twostep gear cone to either of its operative positions.

The locking tooth Illb is somewhat longer than the locking tooth Illa, as shown in Fig. 5, and when the lever III is in the position shown in Fig. 4, the locking tooth I I lb is adapted to engage in one or the other -of two recesses 68a' formed in the arcuate edge of an extension 68b of the lever 68 to lock said lever in one or the other position to which it has been moved in shifting the rear two-step gear cone into either of its operative positions.

The locking tooth lllb, when the lever III is in the position last mentioned, is also adapted to engage in one or the other of three recesses 65a formed in the arcuate edge of an extended portion 65b on the upper side of the lever 65 to lock the lever 65 in one or another of the three positions it assumes in shifting the three-step gear cone to its three operative positions.

When the control lever I04 is in the neutral position, the recess 631) on the under side of the U-shaped portion 63a of the shaft 63 registers with the locking pin I09, whereupon the spring IIOb rocks the lever H0 and the lever III as a unit in a counter-clockwise direction from the position shown in Fig. 4 to the position shown in Fig. 5 at which latter time the locking pin I09 is in its elevated position and the locking teeth I I la and I III) are moved out of locking engagement with respect to the levers 65, 68, and I0, thus allowing said levers to move freely to shift the respective gear cones. After the gear cones have been shifted during the downward movement of the control leverl04 and the levef I04 moved horizontally to a position to cause rotation of the spindle 32 in forward or reverse directions, the recess 63b is out of registry with the locking pin I09, and the latter moves from the position shown in Fig. 5 to that shown in Fig. 4 to move the twopart locking member H0 and III as a unit in a. clockwise direction to lock the levers 65, 68, and I0 against movement.

The levers H0 and III normally move as a unit to function as has just been described, but under certain abnormal conditions it is desirable that the levers have relative movement to each other and the spring H3 is provided to cushion said relative movement and to restore the levers H0 and III to their normal position, as will later be explained.

It is desirable, for efficiency of operation, that, when the control lever Is moved to neutral position to stop the operation of the work spindle for loading and unloading purposes, the spindle be prevented from coasting due to the velocity of the parts forming the spindle drive.' Accordingly, a braking mechanism is provided in the drive for the spindle. It is advantageous that such a braking mechanism be rendered effective automatically by the control lever I04 which brings about the stopping of the spindle and that the braking resistance be automatically variable in proportion to the speeds of operation of the spindle, it being well understood that the greater the speed of operation for the spindle the greater will be the braking resistance required to effect a quick stopping thereof. Mechanism for accomplishing these ends will now be described.

The shaft 40 is provided with a brake drum II4 against which operates a segmental brake shoe II5 carried by a pin Il5a that extends through an opening in a bracket in the head and carries a spring I I5b which constantly urges the brake shoe into brake releasing position. One end of the brake shoe H5 is pivotally connected to a link II6 which in turn is pivotally mounted between spaced lugs I lBa carried by the rear wall of the head. It will be noted that the lugs IlBa are spaced a substantial distance apart so that the end of the link H6 arranged therebetween will be relatively wide, thus imparting stability to the link against lateral movement and holding the brake shoe in alignment with the brake drum. The link H6 adjacent its point of pivotal con nection to the brake shoe H5 is provided with an upstanding cam Il6b which cooperates with a similar downwardly extending cam ll'la. arranged on the under side of a foot member II'I fixedly carried by a rod IIB rotatably and vertically movable in suitable supports in the head and urged upwardly by the spring 8a.. The vertical position of the rod II8 may be adjusted from a position outwardly of the cover of the head by an adjusting screw I l8b provided with a suitable lock nut, as shown in Fig. 15.

The rod III! has fixed thereto a gear segment I I9 which meshes with a rack formed on the end of a forwardly extending portion 60b of the sleeve 60a. which carries the yoke member 60 for shifting the friction clutches for controlling the starting, stopping, and reversing of the work spindle, as previously explained.

It will be seen that when the control lever I04 is moved horizontally to neutral position to disengage the friction clutches, the rod 8 will be rocked by the rack on the portion 60b and the gear segment H9, wherefore the cam I I'Ia will be brought into engagement with the cam Illib, thus depressing the link H6 and applying the brake shoe to the brake drum. When the control lever I04 is swung horizontally away from neutral position, the rod I I8 will again be rocked and the cam II'Ia will move out of engagement with the cam II6b, whereupon the spring II5b will move the brake shoe 5 to brake releasing position.

As previously stated, the braking resistance applied to the brake drum II4 should vary in direct proportion to the speed of operation of the work spindle.

In order that this variation of the braking resistance may be obtained automatically as the operator changes the speeds of operation of the work spindle and in proportion to such speeds, the shaft 83 which is operated by the speed selecting dial BI is provided with an extension 83a, see Fig. 15, supported for rotative movement in a sleeve I20 and having fixed to its end a bevel gear 83b. The sleeve I20 is rotatably mounted in a bearing boss on the under side of the cover 30a and includes at one end a cam I20a and at its opposite end a gear I201).

The cam I 2011 has its periphery in the form of a spiral with points thereon gradually increasing in distance radially from the center of the cam. The lowest and highest points of the periphery of the cam are in relation, respectively, to the lowest and the highest speeds of operation of the work spindle, while the intermediate points of the periphery are in relation to the intermediate speeds of operation of the spindle.

The pointed upper end of a vertically movable rod I2I is in engagement with the periphery of the cam I20a (see Figs. 15 and 10), and the rod is slidably carried by spaced brackets formed in the cover and the head and has fixed to its lower end an L-shaped brake shoe support I22 that is pivotally connected to the end of the brake shoe H5 opposite the end thereof to which the link H6 is pivotally connected. It will be seen that, when the cam I20a is in a position wherein the end of the rod I 2I is in engagement with the lowest point on the periphery of the cam, the rod I2I is in its most upward position.

Assuming that the operator turns the dial 8| to the highest speeds of operation of both series for the work spindle (indicated on the dial in the drawings above the letter N and by the numerals 1316 and 658) the cam I20a will turn by means later to be described so that the end of the rod I 2I now engages the periphery of the cam adjacent its highest point, and consequently the vrod I2I is depressed downwardly and thebrake shoe H5 will accordingly be lowered so that, when the brake shoe is applied by the mechanism previously described, the maximum frictional braking resistance will be provided.

Assuming that the operator turns the dial to obtain the lowest speeds of operation of the two series of the work spindle, that is, to the position indicated by the numerals 52 and 26 shown on the dial 8I below the letter N, the cam I20a will be moved accordingly in the opposite direction from that previously referred to and the end of the rod I2I will engage the periphery of the cam near its lowest point, wherefore the braking resistance of the brake shoe H5, when it is applied to the brake drum H4, will be considerably less than in the instance last referred to.

It will be understood that for the intermediate I speeds of operation of the Work spindle the end of the rod I2I will be inengagement with the periphery of the cam I200. between the lowest and highest points and that the braking resistance of the brake shoe will vary proportionately to the operating speeds of the work spindle.

In order to adjust the braking mechanism to suit varying conditions, the necessary adjustments may be made by means of the adjusting screw I I8?) which is accessible and located outside the head. It will also be understood that in some instances no braking action for the work spindle drive is required, in which event the adjusting screw H8b is moved to a position such that the spring I IBa will move the rod I I8 upwardly where the cam I IIa will not operatively engage the cam H61; and the spring II5b will move the brake shoe away from the drum until a shoulder on the upper side of the brake shoe abuts with the sup-- porting bracket for the pin H5a.

The means for adjusting the cam I20a to vary the braking resistance in proportion to the spec of operation of the work spindle will now be de scribed. The bevel gear 83b on the end of th shaft 83a meshes with a bevel gear 830 fixed to shaft 83d rotatably mounted in the cover 30 and extending in a direction transversely to th shaft 83a (see Fig. 16a). A pair of spools 83 and 831 are splined on the shaft 83d to rotat therewith and move endwise thereon. In Fig. 16 the spools 83c and 83] are shown in a develope view, it being noted that each spool is provide with thirteen steps, one of said steps represent ing the neutral position of the dial 8i and an in active condition of the work spindle when th front two-step gear cone is disengaged therefrorr while the twelve remaining steps relate to th series of spindle speeds indicated on the dial 8| It will be seen that, when the dial 8i is rotate when the gear shifting spools 'I9-I9a and als the spools 83c and 83f are in their outermos position, the shafts 83a and 83d will be rotated as will the spools on said shaft 834 In orde that the endwise movement of the spools 83 and 83) is correlated to the endwise movement of the spools 'l'9-'I9a and controlled by the con trol lever I04, the following arrangement is pro vided:

The disc 98 is provided with a lug of a prede termined length. see Fig. 2, to which is pivotall connected a link 98a adjustable as to length. Th opposite end of the link 98a is provided with fork 98b straddling the ends of levers 98c an 98d. The fork 98b is pivotally connected to th lever 98d by means of a pin, which pin extend through a slot formed in the end of the lever 98 Movement of the link 98a will occasion a sub stantially equalized movement of the levers 98 and 98d. The levers 98c and 98d are fixed t the upper ends of vertically extending rockabl shafts 98c and 98), respectively, while the lowc ends of said rockable shafts have fixed theret laterally projecting lever arms 98g and 98h, se Figs; 15 and 16a. The lever arms 98g and 98l carry at their ends pins engaging the annula grooves in the spools 83c and 83f, respectively It will be seen that when the control lever I0 is raised to move the spools IQ-49a outwardly the spools 83:2 and 83f through the linkage ant levers just described will also move endwise 01 the shaft 83d to their most outward position. A rack bar I203 is slidably mounted in the wall am a bracket of the cover 30a and the rack. portioi thereof meshes with the gear I201) on the sleevi I20 which carries the cam I20a. The rack ba I200 is provided with a laterally extending arn I20d having at its end an upstanding pin I201 located between the spools 83c and 83f.

It will be seen that the spools 83c and BSf, afte they have been moved to their most outward p0 siticn and then indexed by the movement of thl dial 8| to a position relative to the selected spin dle speed, will when they are moved inward]: engage the pin I206 to shift the rackbar I200 and since the rack portion of the latter meshe. with the gear I20b on the sleeve I20, the cam I20: will be adjustably turned to a position such the it will vary the braking resistance in proportioi to the speed of operation of the spindle when th1 latter is next stopped.

In order to more clearly bring out the ncv. features residing in the present invention, thI sequential operation of the machine as thus fai described will now be set forth.

Assuming that the machine is at rest and thl control lever I04 is standing in neutral positior and the dial 8| is positioned with the letter N in line with the pointer 82 with the forward twostep gear cone in the inoperative position, the tongue I06a of the block I06 within the hub I03 is in engagementwith the notch I080, in the stationary block I68, wherefore the control lever I04 is locked against movement horizontally. At this time the rod IZI will be in engagement with the lowest point of the periphery of the cam I20a,

and assuming that the proper adjustment has been given to the screw II5b, the brake shoe is applied to the brake drum II4 with a pressure suitable for the lowest speed. At this time the two-part lever IIO--III will be positioned as shown in Fig. 5 while the locking pin I09 will be in engagement with the recess in the under side of the U-shaped portion 63a of the shaft 63 and the levers 65, 68, and I will be free to move, except that the spools I9 and 19a. are positioned inwardly as shown in Fig. 8, thus holding the levers in their prior position.

The dial 8| is at this time locked against rotation by the locking pin 90 which is in engagement with the periphery of the rod 94. When the operator desires to start the operation of the work spindle, he raises the control lever I04v to its uppermost position to rock the hub I03 about its horizontal axis and through the link ml to rock the disc 98 and the shaft 91 to move the spools I9 and 19a outwardly by means of the equalizer bar 96 to the position shown in Fig. 10, at which time the locking pin 90 is free to move into the recess in the rod 94 to allow the spools to be rotated by the dial. This upward movement of the control lever I 04 acts also through the link 96a to effect a movement of the spools 83c and 83 f to their most outward position. The operator now turns the dial 8| until the number corresponding to the desired speed is in line with the pointer 92, the spools I9 and 19a turning correspondingly during rotation of the dial to bring the proper projections of the spools in line with the pins of the shifting levers, while the turning movement of the spools 83c and 83] brings the proper steps thereon in alignment with the pin I206 of the rack I20c. The operator now moves the control lever I04 downwardly to its lowermost position to bring the spools I9 and a inwardly to shift the shifting levers and the gear cones operated thereby to attain the desired speed and to bring the spools 83c and 83f inwardly to shift the rack bar and adjust the braking resistance. During the downward movement of the control lever I04, the tongue I06a of the block I06 within the hub I03 is swung in a counter-clockwise direction by engagement of the shoe I05 therewith until the tongue IBM has moved out of the notch I08a. and into the segmental groove in the stationary block I08,- as shown in Fig. 4. The operator may now swing the control lever I04 horizontally to engage one or the other of the friction clutches for forward or reverse direction of operation of the work spindle. During this last named movement of the control lever I04, the recesses 63b move out of alignment with the locking pin I09 and the latter is depressed to swing the two-part locking lever IIO-III in a clockwise direction to engage the locking teeth "Ia and I I I b with the locking recesses on the levers 65, 68, and I0. Also during this last mentioned movement of the control lever and the engagement of the friction clutches,

the rod II8 will be rocked through the engagement of the segmental gear II9 with the rack on the extension 60b of the sleeves 60a to cause the cam Illa to move out of engagement with the cam H622 to release the brake.

It will be noted that the work spindle 32 is now operating at the desired speed and work may now be performed and that the spools I9 and 19a and also the spools 83e and 83 are in their most inward position and are locked against rotation by the engagement of the locking pin 90 with the periphery of the rod 94, thus preventing movement of the dial BI and shafts 83a and 63d. It will also be noted that at this time the levers 65, 68, and 10 are locked against movement.

During the operation of the machine at the selected speed, the operator can preselect the speed for the next operation and automatically presets the braking resistance in proportion to such speed in the manner now to be described.

The control lever I04 is raised to its uppermost position without imparting to the lever any horizontal movement. The upward movement of the control. lever. can take place even though the torfgue I060, of the block I06 is in the groove in the stationary block I08 and is not in registry with the notch I08a, since the hub I03 can move relative ,to the block I06 as it merely has a frictional connection therewith through the shoe I05. The upward movement of the lever I 04 moves the spools I9 and 19a to their outermost position, as shownin Fig. 10, as well as the spools 83c and 83],

upper position by the friction shoe I05; The

and the lever will be held in said outward movement of the spools'19 'and'19a will disengage the spools from the pins carried by the levers 65, 68, and I0, but the levers cannot be shifted since they are locked in position by the teeth Ia and I I lb. The outward movement of the spools -03e and 83) releases the pin I206 of the rack bar I200, but since the pin I2I bears against the periphery of the cam Ia there is no tendency for the back bar and the sleeve I20 to move. As previously explained, all the spools are free to rotate when in their outermost position, and the dial may now be turned by the operator to select the desired speed for the next operation of the spindle and to preset the braking resistance, the spring point 89 of the yoke 81 holding the spools and the dial in the adjusted or selected positions. As soon as the first operation has been completed and it is desired to change the spindle speed and braking resistance to that preselected for the next operation, the operator moves the control lever I04 horizontally while elevated to neutral position without imparting any vertical movement thereto. This movement of the control lever I04 disengages the clutch and automatically applies the brake with a braking resistance related to the present spindle speed and acts to disengage the locking teeth I I Ia. and I I ID from locking engagement with the levers 65, 68, and T0 to permit the same to be shifted to shift the gear cones. now brings the lever downwardly to its lowermost position to move the spools I9 and 19a. inwardly to shift the lever 65, 68, or I0 and in turn the gear cones to change the gear ratio for the desired and preselected speed of operation of the spindle. The downward movement of the control lever also brings the spools 63c and 83f inwardly to shift the rack bar I200 to adjust the cam I20a. to vary the braking resistance, when the brake is next applied, in proportion to the new spindle speed. After the downward movement of the control lever has been effected, the lever is moved horizontally to release the brake and to again engage one or the other of the The operator friction clutches to operate the spindle in either because of the engagement of the friction shoe I05 therewith, while the control lever is held in a slightly elevated position and in neutral.

In actual practice, after the next speed for the spindle has been preselected at the proper time, the operator moves the control leverto neutral to stop the spindle drive and continues to move the control lever downwardly to shift the gears and continues this movement horizontally to re-engage the friction clutch to again operate the spindle in forward or reverse direction and at the newly selected speeds. It will be understood that the braking action previously referred to does not at once stop the spindle drive but allows a certain amount of coasting of the spindle drive. However, should the operator delay the continuous downward movement of the control lever after he has brought it to neutral in its upper position, the work spindle drive may stop prematurely, with the result that when the lever is' brought downwardly to shift the gear cone the gears may not properly intermesh while standing still. When this condition occurs, the gear shifting cannot be completed and the lock- .ing teeth Illa. and III?) will engage the high points of the extensions on the levers 55, 68,

.and I0 and not in the recesses formed in the edges thereof. The operator then will give the control lever a horizontal movement to partially engage one or the other of the friction clutches to start the drive momentarily in operation and will then restore the control lever to neutral and quickly bring it downwardly to complete the shifting of the gears.

It will be noted that during the horizontal movement of the control lever I04 while in the partially elevated position just referred to, the two-part locking member- IIOI I I' will be brought inwardly to locking position through the action of the locking pin I09, but, since the teeth Ia and II") are not in registry with the recesses in the extensions on the shifting levers, they'cannot move to a fully locked position. However, inasmuch as the lever IIII may have relative movement with respect to the lever III, the former will be rocked and will compress the spring II3, while the lever III remains stationary. As soon as the control lever I04 has started the spindle drive and has been returned to neutral position, the locking pin I09 moves upwardly into engagement with the recess 83b and the levers H0 and III of the two-part looking member return to the position shown in Fig. 5, the compressed spring II3 acting to move the levers to this position and in conjunction with the spring M02). The parts of the drive are now spinning from the quick engagement and disengagement of the clutch and the control lever can now be brought completely down to fully shift the gears.

There has been described so far a construction wherein the dial 8| and the spools I9 and law are turned manually to select or preselect the different speeds of operation of the work spindle. This turning of the dial and the spools may be accomplished automatically by means of a power mechanism now to be described, which mechanism is'under the control of the control lever I04 which, as will be remembered, moves the spools inwardly to shift the gears and outwardly to allow rotation of the spools, and actuates the friction clutches as well as the brake mechanism for stopping the spindle. The power drive may be operated from a source of power independent of the machine or, as herein illustrated, it may be driven from the pulley shaft of the machine. The pulley shaft 34 is provided adjacent the pulley 33 with a small pulley I23 receiving a belt I24 extending around a smaller pulley I25 carried by a stub shaft I26 rotatably mounted in a housing member I21 secured to the end of the cover 30a of the head, as Viewed in Fig. 2. The stub shaft I26 has fixed to its inner end'a bevel pinion I28 which meshes with a similar pinion I29a fixed on a worm shaft I29 rotatably mounted in the housing member I21 and extending transversely thereof. The shaft I29 is provided with a worm I29a which meshes with a worm wheel I30 carried by a. sleeve I30a freely rotatable on an extension of the previously mentioned shaft'80, the end of the extension of the shaft 30 being supported in the housing member I2I. A clutch member I3I in the form of a sleeve is splined on the sleeve I30a to rotate therewith and have endwise movement thereon. The inner face of the clutch member I3I is provided with a plurality of spaced, narrow clutch teeth I3Ia which, when the clutch member I3I is moved in one direction, lie between widely spaced clutch teeth I32 projecting from the outer face of a star wheel I32a fixed to the extension of the shaft 80. The clutch member I3I is moved axially of the sleeve I30a by means of a lever I33 having a shoe I33a at its lower end engaging a circular groove in the clutch member I3I, while the upper end of the lever I33 is fixed to a stub shaft that is rockably'mounted in a boss inthe side wall of the housing member I21 I the head and supported in the wall thereof and by a lug arranged within the cover. A spring I35a'is arranged on the rod I35 outwardly of the cover and between the wall thereof and the fork on the rod, and said spring acts at all times to urge the clutch into a disengaged position. Intermediate the wall and the lug which supports the rod I35 and within the cover 30a, the rod is provided with a collar I351) fixed thereto, see Fig. 2.

The sleeve 93 previously referred to is provided with a downwardly extending portion 93b, see Fig. 4, which has at its lower end a forked portion straddling the rod I35, as clearly shown in Figs. 2 and 4. The portion 93b of the sleeve 93 straddles the rod I35 between the collar I351; and the end wall of the cover 30a, wherefore, when the spools I9 and 19a are moved to their outermost position by the upward movement of the control lever I 04, the sleeve 93 moves in a. direction such that the portion 93b will slide along the rod I35 toward the collar I35b, and just prior to the end of the movement of the sleeve 93, theportion 93b abuts the collar I352) and moves the rod against the tension of the 7 spring I35a, thus causing the clutch member I3I, through the levers I34 and I33, to move toward the star wheel I32a and to position the teeth I3Ia between the widely spaced teeth I32 to drive the shaft 80. .(see Figs. 2 and 9), wherefore, the star wheel I32a, the spools I9, 19a, and the dial 8| are rotated by power.

As has been previously explained, the teeth I3Ia of the clutch member I3I are relatively narrow as compared with the spaces between the teeth, while the teeth I32 on the star wheel I32a are also widely spaced apart. A lever arm I36 is pivotally mounted in the housing member I21 and carries at its free end a roller I36a which engages the peripheral teeth of the star wheel (see Fig. 3) and a spring I36?) acts to urge the roller I36a into engagement with the peripheral teeth of the star wheel.

Assuming the teeth I3Ia of the clutch member I3I have engaged the clutch teeth I32 of the star wheel I32a, the star wheel will be turned and the roller I36a will ride over the high point of a peripheral tooth of the star wheel, where upon the spring I361), acting upon the lever I36, imparts to the star wheel a movement ahead of the driving movement, with the result that the rotation of the star wheel is intermittent, inasmuch as the slowly operated clutch member only drives the star wheel until the roller passes the high point of the peripheral tooth, whereupon the spring I36b causes the star wheel to jump ahead of the clutch drive, providing momentary periods of rest for the star wheel.

It will be remembered that the dial BI is operatively connected with the shaft 80 and the star wheel I32a and hence the intermittent movement of the star wheel moves the dial intermittently, wherefore, the operator has sufficient time to disengage the power drive for the dial movement when the dial has turned to theproper position for the desired speed for the work spindle. It will also be noted that the intermittent movement thus imparted to the shaft 80 results in an intermittent or step-by-step rotation of the spools I9 or 19a and through the shafts 83a and 83d of the spools 83c and 83f.

In the operation of the machine when equipped with the power drive for the spool shaft 80 and dial M, as just described, the operator raises the control lever I04 to its most upward vertical position to bring the spools I9, 19a, 83c, and 83 to their outermost position and to start' the power drive for the shaft 80 during the last portion of the upward movement of the lever. With the control lever in its upper position and the power drive imparting the step-by-step rotative movement to the dial 8I and spools I9, 19a, 83a and- 83 the operator watches the dial until it has turned to bring the numeral representing the speed desiredin line with the pointer 82, whereupon he moves the control lever I04 slightly downwardly to disengage the clutch I3I from the star wheel I 32a and thus stop the intermittent drive of the shaft 80 and the dial 8I. In instances where the operator is preselecting the speed of operation for the next operative step of the spindle, he merely brings the control lever I 04 downwardly sufficiently far to disengage the clutch I3I, as has been stated, and then when the current operation of the work spindle has reached its conclusion, he moves the control lever to neutral position, as will be remembered, to disengage the friction clutch and apply the brake,

and then downwardly to bring all of the spools inwardly to shift the gear cones to change the speed of the spindle to the preselected speed and to preset the braking resistance, after which the operation is continued, as has been previously set forth, by shifting the control lever horizontally to release the brake and to connect the power drive to the work spindle in forward or reverse direction.

Reference should now be made to Figs; 18 to 25, inclusive, wherein is shown a modified form of construction from that previously described. The modified construction will now be described, and it will be noted that it differs from the former construction in that it-employs a pair of spools for shifting each gear cone, thus using three pairs of spools, while the former construction employed only a single pair of spools for shifting all of the three gear cones.

The dial 8| in the modified construction is in substantially the same location and serves the same purpose as the dial 8| in the construction previously described. In the second instance, however, the dial is fixed to a shaft I31 extending horizontally into the cover 301) of the head and'having. fixed to its inner end a bevel gear I38 which meshes with a bevel gear I39 fixed to the end of a horizontal shaft I40 rotatably mounted in the cover 30b, see Fig. 20. The bevel gear I39 is formed on a sleeve which also has formed thereon, inwardly of the bevel gear, a spur gear I39a and, outwardly of the bevel gear, a second spur gear I391). The spur gear I39a meshes with the spur gears I4I and I42 fixed to parallel rotatable shafts I4Ia and I42a mounted in the cover 301), as shown in Fig. 25, while the outer spur gear I39b meshes.

with a spur gear I43 fixed to the end of a rotatable shaft I43a parallel to the shafts I40, I4Ia, and I42a. The ratio between the spur gear I39a and the spur gears I4I and I42 is one to one, while between the spur gear I39b and the spur gear I43 it is two to one, in other words, the gears MI and I42 with their shafts I4Ia. and I42a are given one complete revolution for a complete revolution of the dial, while the gear I43 with its shaft M311 is given two revolutions for a complete revolution of the dial, it being noted that the bevel gears I38 and I39 are of equal size.

The shaft I4Ia has splined thereto a pair of spools I44 and MM, see developed view in Fig. 24, which control the shifting of the rear two-step gear cone. The shaft I 42a has splined thereto a pair of spools I45 and MM, see Fig. 18 and developed view in Fig. 23, which control the shifting of the front two-step gear cone, while the shaft I 43a hassplined thereto a pair of spools I46 and MM, see Fig. 20 and the developed View of Fig. 22, which control the shifting of the threestep gear cone.

The shafts. I4Ia, I42a. and M30. are arranged at equal radial distances with respect to the shaft I40, wherefore circular flanges M111 and H811 formed adjacent the outer ends of members I41 and I48 freely slidable on shaft I40 engage in grooves formed in each of the spools just referred to (see Figs. 18 and 20) so that, when the members I41 and I48 are moved equal distances inwardly and outwardly on the shaft I40, the three spools I44a, MM, and M61: are moved by the member I48 and the three spools I44, I45, and

I46 are moved by the member I41.

In order to move the members I41 and I 48 inwardly and outwardly equal distances on the and I50. It will be seen that movementof one gear segment to move its associated rack member will impart a corresponding movement to the other gear segment and its associated rack member and will, therefore, impart equal movements to the members I41 and I48.

The gear segment I49 is fixed toa rockable shaft I5I mounted in the cover 3017 of the head and extending above the. upper side of the same where it has fixed thereto a disc I52 (see Fig. 18). The gear segment I50 is carried by a vertical stub shaft I500. mounted in suitable brackets in the cover 301). The disc I52 is similar to the disc 98, previously described, except that the rod I53, similar to the rod 99, is connected to and extends from the disc I52 in the opposite direction, as clearly shown in Fig. 21. The rod I53 is pivotally connectedto a part Ia of a two-part link and in turn said part is adjustably connected to a second part IOIa of the two-part link, the two-part link corresponding to the twopart link I00-IOI previously described, and being connected to the hub I03a by the fork I02a. in the same manner as in the first described embodiment. The hub I03a is identical with the hub I03 previously described and has connected thereto the control lever I04a, similar to control lever I04, which extends beyond the front of the head above the dial 8|.

The shifting lever I54 for the front two-step gear cone is identical with the shifting lever 10 previously described, and is actuated by the spools I45 and H511 through the medium ofa pin I55 arranged between the spools I45-I45a and carried by a lever arm I56 similar to the lever arm 15 previously referred to;

The lever arm I56 is connected through a link I51 similar to the link 14 with a lever arm I58 similar to lever arm 13 and operatively connected with a vertically extending shaft I59 that has fixed to its lower end the shifting lever I54.

The rear two-step gear cone is shifted by the spools I 44--I 44:; through the medium of a pin- I60 arranged between said spools and carried by a lever arm I6I similar to the lever arm 63 previously described.

The three-step gear cone is shifted through the medium of a pin I62 located between the spools I46--I46a and carried by a lever arm I63 similar to lever arm 61 and fixed to a vertically extending rockable shaft I64 which has fixed to its lower end a shifting lever I65 that is operatively connected with the three-step gear cone and corresponds to the shifting lever 65.

The shifting levers- I54, I6I, and I65 are provided with recessed extensions into which engage the teeth I I la and I I Ib in exactly the'same way as do the similar teeth with respect to the levers 65, 68, and 10.

In this embodiment, the various parts not specifically referred to operate and function in exactly the same way as do the corresponding parts in the embodiment previously described. It will be understood that the brakingmechanism and also the power drive for the dial described with reference to the first embodiment can be applied to the embodiment just explained, but, since they are the same in both instances, they are not illustrated with respect to the second embodiment in order to avoid mere repetition.

It will be noted in connection with the modified form of construction that three pairs of spools are employed for shifting the gear cones instead of the one pair used inthe first embodiment. Therefore, the three series of projections formed which carries at its outer end a block on the spools of the single pair of the first embodiment have been separated and applied respectively tothe individual pairs of spools of the second embodiment. In addition, the spools of the pair which control the shifting of the threestep gear cone are given two rotations for one rotation of the dial, wherefore, the projections of said spools may be made coarser and will function twice for each complete revolution of the dial.v

Inasmuch as the three-step gear cone must have a neutral point and the spools for controlling said cone make two revolutions for one revolution of the dial, then the spools for controlling the twoto obviate this difficulty, it is proposed, if desirable, to employ power means controlled by the previously described movements of the control lever I041) for moving the spools endwise and for shifting the gears.

In Figs. 26 and 27 there is illustrated a power means for this purpose in the form of a hydraulic motor controlled by the movements of the control lever I041). The cover 300 of the head has fixed to its upper side a cylinder I66 in which operates a piston I61 fixed on the end of a piston rod I61a I611) having a transverse slot formed therein. A lever I68 is fixed to the upper end of the rockable shaft that actuates the spools inwardly and outwardly, similar to the shafts 91 and II, and said lever I68 is provided adjacent its end with an upstanding roller I68a engaging in the transverse slot in the block I61b, wherefore, inward and outward movements of the piston I61 effect a rocking movement of the lever I68 and endwise movements of the spools.

The cylinder I66 is provided with ports I66a and I66b on opposite sides of the piston I61 and said ports are connected by conduits I69 and I with r the body of a control valve I1 I. The body of the control valve I1 I is also connected by suitable conduits I12 and I13 with the source of fluid under pressure, including a pump, not shown, having the usual bleeding valve.

The passage of the pressure fluid through the valve body and the conduits I69 and I10 is controlled by a valve proper I1Ia carried by a 'rod projecting outwardly of the front of the valve body and connected with a bell-crank lever I14 having an arm I14a'extending beneath an extended portion I030 on the rear of the hub l03b.

A spring I acts to move said bell-crank I14 to the position shown in Fig. 2'7 when the control lever I041) is in its lower or substantially horizontal position.

It will be understood that when the control lever I041) is elevated by the operator, the valve proper will be so positioned that the pressure fluid will fiow into the cylinder I66 at the proper side of the piston I61 to move said piston in the required direction to rock the lever I68 to move the spools an equal distance outwardly to allow the same to be indexed, and when the control lever ND is moved vertically downwardly, the valve proper will be shifted by the spring I15 so that a reverse direction of movement of the piston I61 will take place and the spools will be moved inwardly to shift the gears in the spindle drive; It will be noted that the extended portion I030 of the hub I03b is of arcuate shape, wherefore, the hub I031) can be rocked horizontally bythe control lever Illflb for forward or reverse drives of the spindle and in such position can be elevated and the extended portion I030 brought into engagement with the arm I'Ma of the bellcrank m.

It will be understood that the means for operating the spools by power to index the same (as shown in Fig.2) may be readily used in combination with the hydraulic means for moving the spools endwise, as has just been described. It will be further understood that the braking means for the spindle drive previously explained may be used with the embodiment employing the hydraulic motor for shiftingthe spools endwise.

It will be remembered that the rods 99 and I53, the two-part links I00II)| and IIlIla-IOIa and forks I 02-Ill2a. are adjustable with respect to the members to which they are connected or, in the case of the links, with respect to the two parts thereof. The adjustability of these parts enables the leverages of the rods and the forks to be varied while the length of the two-part link may also be varied. This adjustability is provided to regulate the leverages and link connections so that the upward movements of the control levers I06 and I 04a to their most upper positions act to bring the spools, both in the form employing a single pair of spools and in the form employing three pairs of spools, to their most outward or separated positions. The adjustability also enables the most inward position of the spools to be definitely related to the position of the control levers when the latter are in a substantially horizontal position with respect to the head.

The advantages of the arrangement just referred to are that the parts can be made for different heads and with varying leverages and then can be adjusted to suit the conditions incident to the particular head and the required movement of the spools for the heads ofvarious machines.

It will be remembered that, in the particular machines described, the gear train for the spindle drive is such that twelve different speeds of operation can be imparted to the spindle both when the driving motor is operated at high speed and at loW speed and by means of three shiftable gear cones. Therefore, in order to obtain certain speeds of operation of the spindle, it will be necessary, after selecting or preselecting the desired speed, to shift two or more of the gear cones.

Inasmuch as the shifting of the gear cones is accomplished by a single movement of the control lever and the inward movement of the spools, it will be seen that, unless provision is otherwise made, the gear train in the drive for the spindle will be broken at two .or more points simultaneously, which might result in an undesirable slowing up or stopping of certain parts of the gear train, and, therefore, may, if the gears should not correctly mesh, prevent the shifting of the gear cones.

Provision has been made to obviate this difliculty' in the machines embodying the invention by,designing the lengths of the projections on the spools in such manner that the pins effecting the shifting of the various gear cones are shifted in a predetermined sequence. In addition to this,

the shifting levers associated with said pins are of predetermined length to further assure the desired predetermined sequence of shifting movement for the gear cones.

The shifting levers BI and I63, which respectively shift the three-step gear cones in the form employing a single pair of spools and in the form using three separate pairs of spools, are relatively short and therefore effect a, quick shifting movement of the three-step gear cones.

The shifting levers'68 and ISI for shifting, respectively, the rear two-step gear cones in both forms, are longer than the levers 61 and I63 and, therefore, shift the rear two-step gear cones more slowly than the three-step gear cones are shifted by their shifting levers.

The shifting levers I5 and I56 for thefront twostep gear cones are relatively long and act through the links M andv I51 and the relatively short intermediate levers I3 and I58 upon the levers l0 and I56 which are relatively long. In this instance there are long levers acting through short levers upon long levers, with the result that the shifting movements of the front two-step gear cones are slower than the shifting movements of the rear two-step gear cones and much slower than the shifting movements of the three-step gear cones.

The sequence in which the gear cones will be shifted may be stated as follows: 7

The gear cone which is nearest the pulley shaft or power drive 3 3, in this instance the three-step gear cone, will be shifted and a gear thereon brought into partial engagement with its new mating gear before the rear two-step gear cone has been shifted out of engagement with its old mating gear, while the new gear on the rear twostep gear cone-will be partially engaged with its new mating gear before the old gear on the front two-step gear cone has moved out of engagement with its old mating gear. In other words, where two or more of the gear cones are to be shifted, the cone nearest the source ofpower (the pulley shaft) will be shifted first and brought partially into engagement with a new mating gear before the next cone in the drive train which is to be shifted has been moved out of engagement with its old mating gear. In this way the gear train, regardless of the number of gear cones to be shifted, will never be broken in more than one place at a time.

It will be understood that, although the drive train for the spindle has been illustrated herein as including three gear cones, the invention may be applied to and will function equally as efficiently in a drive train employing a greater or a lesser number of gear cones.

Although several embodiments of the invention have been illustrated and described herein, it will be understood that the invention is not to be limited thereto and that it is susceptible of various modifications and adaptations within the scope of the appended claims.

Having thus described my invention, I claim:

1. In a machine tool having. a part to be moved at different speeds, driving means for moving said part, speed changing means for said part including a device movable in one direction during the movement of said part to preset it for a certain speed and movable in another direction when said driving means is disconnected from said part to actuate said speed changing means to obtain said speed, and a single control member for controlling said device during its latter movement and for controlling said driving means. 

